System and method for determining inertia properties of a rigid body

ABSTRACT

System for determining inertia properties of a rigid body, particularly the inertia tensor, the mass and/or the position of the center of mass, comprising: a carrier ( 10 ), which is designed for suspending a rigid body ( 2 ) from the carrier ( 10 ), such that the rigid body ( 2 ) is able to perform movements along the six degrees of freedom of the rigid body (B), at least six sensors ( 100 ) providing output signals for detecting the movement of the rigid body ( 2 ) along the six degrees of freedom of the rigid body ( 2 ), a measuring device ( 110 ) cooperating with the sensors ( 100 ), wherein the measuring device ( 110 ) is configured to measure said movement of the rigid body ( 2 ) by means of said output signals (ŝ 1 (t k )), and an analysing means ( 20 ) configured for determining from said output signals (ŝ 1 (t k )) said inertia properties (r s ). Furthermore, the invention relates to a method for determining the inertia properties (r s ).

The invention relates to a system for determining inertia properties ofa rigid body r_(s)={m, ζ_(G), θ}—also called rigid body properties—,particularly the inertia tensor θ (moments of inertia), the mass mand/or the position of the center of mass (gravity) ζ_(G), as well as toa method for determing said properties of a rigid body.

These rigid body properties are essential in predicting and optimizingthe dynamic behaviour of various types of machines. Examples include theprediction of roll-over limits of vehicles, the reduction of enginevibrations through optimal mounts, and the design of optimal actuationand control systems for robot manipulators, aircraft, and satellites.

Therefore, the problem underlying the present invention is to providefor a system and method of the afore-mentioned kind, which allows fordetermining said inertia properties in a simple, cost effective andaccurate manner.

This method is solved by a system having the features of claim 1.

According thereto, the system according to the invention comprises: acarrier which is configured and provided for suspending a rigid bodyfrom said carrier, such that the rigid body is able to perform movementsalong the six degrees of freedom of the rigid body (it is also possibleto restrict the movements to a smaller number of degrees of freedom), atleast six sensors (or a number of sensors corresponding to the number ofdegrees of freedom of the rigid body) providing output signals fordetecting the movement of the body along the considered degrees offreedom of the rigid body, a measuring device cooperating with thesensors, wherein the measuring device is configured to measure saidmovement of the body by means of said output signals, and an analysingmeans cooperating with said measuring device configured forautomatically determining from said movement or rather output signalssaid interia properties.

Particularly, the measuring device stores and eventually displays valuesof said movement corresponding to the output signals provided by thesensors. The measuring device can be formed by a computer that runs asuitable software that is particularly loaded into the computers memoryand comprises an interface for making connection to the sensors, i.e.,so that output signals of the sensors can be read out and properlyassigned and further proceeded by the software.

Likewise also the analysing means can be formed by said computer and acorresponding software running on said computer, which software may alsobe used for measuring said movement (motion) of the rigid body.

Preferably, elastic elements or elements providing for a restoring forceare designed and provided for suspending the rigid body in a way that(free) vibrations along the six degrees of freedom (or a smaller numberof degrees of freedom) of the rigid body result, when the rigid body isexcited to move, for instance by pushing it in some direction.

In this respect, the measuring device is preferably configured tomeasure as said movement output signals of sensors corresponding to thetranslation of the rigid body, whose intertia properties shall bedetermined, along the three orthogonal axes as well as the rotationsabout these axes as a function of time (in case six degrees of freedomare considered). Preferably, the considered time is discretized into aplurality of discrete points in time t_(k).

In a preferred embodiment, said analysing means is designed and providedto fit said measured output signals ŝ₁(t_(k)) to a function in the formof

${s_{l}\left( t_{k} \right)} = {A_{l}{\sum\limits_{j = 1}^{6}\; {X_{j}{^{{- \zeta_{j}}\omega_{j}t_{k}}\left( {{a_{{2j} - 1}{\sin \left( {\omega_{j}t_{k}} \right)}} + {a_{2j}{\cos \left( {\omega_{j}t_{k}} \right)}}} \right)}}}}$

that corresponds to a theoretical model of the measured movement (sensoroutput) ŝ₁(t_(k)) of the suspended vibrating rigid body. Here, the sumcorresponds to the rigid body motion.(Note that in case less than sixdegrees of freedom are considered, the above equation changesaccordingly, i.e., the summation runs from j=1 to the respective numberof considered degrees of freedom).

In the above Equation A₁ (1 labels the sensors) is a matrix of constantsrelating the rigid body motion to the measured output signal ŝ₁(t_(k))(corresponding to the sensor output, i.e., the output signals of thesensors) at time step t_(k), in particular.

Further, particularly, co_(j) denotes the six (j=1, . . . , 6) naturalfrequencies (eigenfrequencies), and ζ_(j) denotes the damping ratio ofthe j-th rigid body mode in particular. Finally, a_(2j−1) and a_(2j)represent the amplitude and phase of a given mode j, in particular.

In order to determine said inertia properties of the rigid body, theanalysing means is preferably designed and provided to minimize anexpression in the form of

$\sum\limits_{l = 1}^{N_{l}}\; {\sum\limits_{k = 1}^{N_{k}}\; \left( {{s_{l}\left( t_{k} \right)} - {{\overset{ˇ}{s}}_{l}\left( t_{k} \right)}} \right)^{2}}$

with respect to the inertia properties r_(s) ∈

, the above stated amplitude and phase {a_(i)} ∈

, and the damping ratios {ζ_(j)} ∈

, i.e., r_(s), a_(j), and ζ_(j) are varied in order to minimize saidexpression.

Once the proper minimum is reached r_(s) equals the actual inertiaproperties of the suspended rigid body. Here, N₁ is the number ofsensors, and N_(k) is the number of considered (measured) time stepst_(k).

Preferably, the analysing means is particularly configured to conductsaid minimisation by means of a non-linear least-squares method.

The system according to the invention preferably comprises elasticelements, which are designed for suspending the rigid body from thecarrier, wherein the rigid body is suspended from the carrier via saidelastic elements. Preferably, each of the elastic elements extendslongitudinally along an associated extension direction.

In particular, these elastic elements are designed as (suspension) wiresor (coil) springs or a combination thereof—for instance a coil springconnecting two free end portions in the form of longitudinally(linearly) extending wires.

It is possible to use one, two, three, four, five, six, seven or eightor even more elastic elements for suspending the rigid body.

In a further embodiment of the invention, the system comprises aplatform or a similar element that is configured and provided forsupporting the rigid body whose inertia properties shall be determined.Then, said elastic elements connect the carrier to the platform on whichsaid rigid body rests, i.e., the rigid body is suspended from thecarrier via the platform and the elastic elements.

In order to measure said excited movement of the suspended rigid body,said sensors may be directly attached to the platform or to the carrieror to the rigid body itself. Alternatively each sensor can be made partof an elastic element, so that the sensor is attached to the carrier andthe platform (if present) via a portion of the respective elasticelement, respectively.

In a further embodiment of the invention, the carrier (also calledsupport or support frame) is essentially designed as a hexahedralframework.

Furthermore, the problem according to the invention is also solved by amethod for determining the stated inertia properties of a rigid body(rigid body properties) having the features of claim 10, wherein thesystem according to the invention is preferably used for conducting themethod.

The method according to the invention comprises the steps of: suspendingthe rigid body from a carrier, forcing the rigid body to performmovements along the six degrees of freedom of the rigid body (or lessdegrees of freedom, see above), measuring said movement of the rigidbody automatically, i.e., particularly by means of some sort of ameasuring device (see above) comprising sensors or cooperating with thelatters, and determining said rigid body properties from said movement(output signals) automatically, i.e., particularly by means of some sortof an analysing device (see above), wherein particularly the rigid bodyis suspended such that it performes a movement (motion) in the form offree vibrations when excited, wherein particularly measuring saidmovement corresponds to measuring output signals of sensorscorresponding to the translations of the rigid body along threeorthogonal axes and the rotations of the rigid body about these axes asa function of time (in particular as a function of discretized timet_(k)) in case six degrees of freedom are considerd.

Preferably, said measured movement (output signals) ŝ₁(t_(k)) is fittedto a function of the form

${s_{l}\left( t_{k} \right)} = {A_{l}{\sum\limits_{j = 1}^{6}\; {X_{j}{^{{- \zeta_{j}}\omega_{j}t_{k}}\left( {{a_{{2j} - 1}{\sin \left( {\omega_{j}t_{k}} \right)}} + {a_{2j}{\cos \left( {\omega_{j}t_{k}} \right)}}} \right)}}}}$

that models the sensor output signals (measured by the measuringdevice), wherein said rigid body properties are (automatically)determined by (automatically) minimizing an expression in the form of

$\sum\limits_{l = 1}^{N_{l}}\; {\sum\limits_{k = 1}^{N_{k}}\; \left( {{s_{l}\left( t_{k} \right)} - {{\overset{ˇ}{s}}_{l}\left( t_{k} \right)}} \right)^{2}}$

with respect to r_(s) ∈

, {a_(j)} ∈

, {ζ_(j)} ∈

, wherein said minimisation is particularly (automatically) conducted bymeans of a non-linear least-squares method. Here, N₁ is the number ofsensors, and N_(k) is the number of considered (measured) time stepst_(k).

Advantageously, besides measuring said movement of the suspended andvibrating rigid body, merely the following parameters are preferablyused for determining the inertia properties of the considered rigidbody:

-   -   the number (N_(p)) of the elastic elements (p),    -   the stiffness value of the elastic elements (k_(p)),    -   the lengths (l_(p)) of the unloaded elastic elements (p),    -   the attachment locations (ζ_(a, p)) of the elastic elements (p)        on the carrier (10), particularly in space-fixed coordinates,    -   the attachment locations (ζ_(b,p))of the elastic elements (p) on        the platform (30) or the rigid body (S), particularly in        body-fixed coordinates,    -   the orientation of the field of gravity (ñ_(g)), and    -   the rigid body properties (r_(p)) of the platform (when        present).

It is a remarkable advantage that these paremeters remain constant for agiven system (carrier and suspended platform) for all measurements.

Further advantages and details of embodiments of the present inventionshall be explained in the following with reference to the Figures,wherein

FIG. 1 shows a perspective schematical view of a system according to theinvention;

FIG. 2 shows a directly suspended rigid body;

FIG. 3 shows a rigid body being suspended via a platform supporting therigid body;

FIG. 4 shows a platform with sensors attached to it;

FIG. 5 shows a modification of the system according to FIG. 4, whereinthe sensors are attached to the carrier; and

FIG. 6 shows a further modification of the system according to FIG. 4,wherein the sensors form part of the elastic elements used forsuspending the rigid body;

FIG. 1 shows in conjunction with FIGS. 2 to 6 a system 1 that isdesigned and provided for determining (estimating) the rigid bodyproperties (inertia properties) of a mechanical structure (rigid body2), which are defined by

r={m, ζ_(G), Θ},   (1)

where m is the mass, ζ_(G) is the location of the center of gravity, andθ is the inertia tensor about the center of gravity

$\begin{matrix}{\Theta = {\begin{bmatrix}I_{11} & \; & {{sym}.} \\I_{12} & I_{22} & \; \\I_{13} & I_{23} & I_{33}\end{bmatrix}.}} & (2)\end{matrix}$

These ten parameters define a complete model of the structure's (rigidbody's) rigid dynamic behavior.

In order to determine the inertia properties of the rigid body 2 thelatter is suspended in elastic elements p in the form of wires, eitherdirectly (cf. FIG. 2) or via a rectangular platform 30 that serves as asupport for the rigid body 2 (cf. FIG. 3). The number and arrangement ofthe suspension wires p can be freely chosen. Preferably, the wirestiffness k_(p) should be low in order to ensure that the structure(rigid body) 2 has six rigid body mode shapes X_(j) (i.e., there are noelastic deformations of the test object (rigid body)); moreover, thewire stiffness k_(p) is preferably chosen to be constant (theforce-displacement-relationship is linear) and damping should be light.The combination of soft metal coil springs with more or less rigid wiresis one way to meet these requirements.

According to FIG. 1, the rigid body 2 is suspended from a carrier 10 inthe form of a hexahedral framework having an upper rectangular frame 11connected to a lower rectangular frame 12 via four vertically extendinglegs 112 (related to a state of the carrier in which the latter ispositioned as intended), wherein each leg 112 connects a corner of thelower frame 12 to an associated opposing corner of the upper frame 11.

For suspending the rigid body 2, a platform 30 for supporting the rigidbody 2 is provided, wherein said plaform 30 is suspended from thecarrier 10 by means of 8 elastic elements p, wherein each of the 8elastic elements p is fixed with a free end to the upper frame and withan opposing free end to an edge 31 of the platform 30, such that elasticelements connected to the same edge 31 run preferably parallel withrespect to each other.

After suspending the test object (rigid body) 2, preferably freevibrations of the six rigid body modes j are initiated in a randomfashion, for example by pushing the structure 2 in an arbitrarydirection. The motion (movement) of the rigid body 2 in the course ofthe resulting free vibration is measured about each of the six rigidbody degrees of freedom (DOF)(or about a smaller number of degrees offreedom) by means of sensors 100 and a measuring device 110 connectedthereto. In FIG. 1 all six sensors 100 are indicated as a square at oneelastic element of the upper frame 11 (note that there are eight wires(elastic elements) p in FIG. 1 but only six sensors 100).

Possible sensor arrangements are depicted in FIGS. 4 to 6. The measuringdevice 110 hands the measured movement (output signals) over to ananalyzing means 20 that determines the desired inertia properties r_(s)(cf. Equation (1)). Both the measuring device 110 and the analysingmeans 20 can be formed by a computer 130 on which a suitable softwarefor measuring said movement and determing said rigid body propertiesr_(s) is carried out.

In addition to the motion (free vibrations) of the rigid body 2, inparticular only the following parametes need to be known in order todetermine the rigid body properties r_(s):

-   -   the number of suspension wires N_(p),    -   the wire stiffness value k_(p),    -   the lengths l_(p) of the unloaded wires,    -   the attachment locations ζ_(a,p) on the structure (rigid body)        2,    -   the attachment locations {umlaut over (ζ)}_(b,p) on the platform        (support) 30,    -   the orientation ñ_(g) of the field of gravity,    -   the rigid body properties r_(p) of the platform (if used).

Note that none of these parameters changes over the lifetime of a system1 of the type shown in FIG. 1.

Assuming now small displacements and negligible damping effects, themotion of a suspended rigid body 2 is defined by

$\begin{matrix}{{{{M\begin{bmatrix}{\delta \; \overset{¨}{x}} \\{\delta \; \overset{¨}{\theta}}\end{bmatrix}} + {K\begin{bmatrix}{\delta \; x} \\{\delta \; \theta}\end{bmatrix}}} = \begin{bmatrix}f \\t\end{bmatrix}},} & (3)\end{matrix}$

wherein δx is a reference point displacement (3×1 vector), δθ is arotation about the coordinate axes (3×1 vector), f is a translationalforce (3×1 vector), t is a moment of force (3×1 vector), M is the massmatrix (6×6 matrix),and K is the stiffness matrix (6×6 matrix).

Note that in case of large displacement amplitudes one may use insteadof Equation (3) the complete non-linear equations of rigid body motion.In this case one may numerically integrate these Equations in order toderive a method equivalent to the harmonic approach presented below.

Both the mass matrix M and the suspension stiffness matrix K arefunctions of the unknown rigid body properties r_(s). The mass matrix Mof the rigid body 2 is now defined as

$\begin{matrix}{{M(r)} = \begin{bmatrix}{mI} & {- {m\left\lbrack \zeta_{G} \right\rbrack}_{x}} \\{m\left\lbrack \zeta_{G} \right\rbrack}_{x} & {\Theta - {{m\left\lbrack \zeta_{G} \right\rbrack}_{x}\left\lbrack \zeta_{G} \right\rbrack}_{x}}\end{bmatrix}} & (4)\end{matrix}$

wherein the notation [ ]_(x) used in Equation (4) transforms a crossproduct into a matrix vector multiplication a×b=[a]_(x)b, where

$\begin{matrix}{\lbrack a\rbrack_{\times} = {\begin{bmatrix}0 & {- a_{3}} & a_{2} \\a_{3} & 0 & {- a_{1}} \\{- a_{2}} & a_{1} & 0\end{bmatrix}.}} & (5)\end{matrix}$

In case a platform 30 is used, the overall mass matrix M is composed ofthe unknown rigid body properties of the test object 2, r_(s), and theknown rigid body properties of the platform r_(p)

M=M(r _(s))+M(r _(p))   (6)

The stiffness matrix K depends on the unknown overall mass and center ofgravity,

$\begin{matrix}{m = {m_{S} + m_{P}}} & (7) \\{\zeta_{G} = {\frac{1}{m}{\left( {{m_{S}\zeta_{G,S}} + {m_{P}\zeta_{G,P}}} \right).}}} & (8)\end{matrix}$

The stiffness matrix K also depends on the static equilibrium positiondefined by the location x₀ and orientation θ of the space-fixedcoordinate system spanned by ({tilde over (e)}₁, {tilde over (e)}₂,{tilde over (e)}₃) relative to the body-fixed coordinate system spannedby (e₁, e₂, e₃) (cf. FIG. 2). The parameters x₀ and θ are used totransform the space-fixed coordinates into body-fixed coordinates asfollows,

ζ_(b,p) =x _(Õ) +R(θ)^(T){tilde over (ζ)}_(b,p)   (9)

n _(g) =R(θ)^(T) ñ _(g),   (10)

where R(θ) is a rotational transformation matrix.

$\begin{matrix}{{R(\theta)} = {{\begin{bmatrix}1 & 0 & 0 \\0 & {\cos \; \theta_{1}} & {\sin \; \theta_{1}} \\0 & {{- \sin}\; \theta_{1}} & {\cos \; \theta_{1}}\end{bmatrix}\begin{bmatrix}{\cos \; \theta_{2}} & 0 & {{- \sin}\; \theta_{2}} \\0 & 1 & 0 \\{\sin \; \theta_{2}} & 0 & {\cos \; \theta_{2}}\end{bmatrix}}\begin{bmatrix}{\cos \; \theta_{3}} & {\sin \; \theta_{3}} & 0 \\{{- \sin}\; \theta_{3}} & {\cos \; \theta_{3}} & 0 \\0 & 0 & 1\end{bmatrix}}} & (11)\end{matrix}$

The static equilibrium position (x₀,θ) is not measured, but instead isobtained by minimizing the potential energy function

$\begin{matrix}{{V\left( {x_{\overset{\sim}{O}},\theta} \right)} = {V_{g} + {\sum\limits_{p = 1}^{N_{p}}{V_{e,p}.}}}} & (12)\end{matrix}$

In Equation (12), V_(e,p) represents the elastic energy stored in agiven elastic element (wire) p,

$\begin{matrix}{{V_{e,p} = {\frac{1}{2}{k_{p}\left( {l_{p} - {\zeta_{{ba},p}}} \right)}^{2}}},{where}} & (13) \\{\zeta_{{ba},p} = {\zeta_{a,p} - {\zeta_{b,p}.}}} & (14)\end{matrix}$

The term V_(g) in Equation (12) represents the gravitational energy ofthe rigid body 2 and is defined by the projection of the gravity force,mgn_(g), onto the vector x₀−ζ_(G) that points from the center of gravityto the space-fixed origin Õ.

Once the static equilibrium position has been determined by minimizingEquation (12), the stiffness matrix K is obtained as follows

$\begin{matrix}{{K = {{- {\sum\limits_{p = 1}^{N_{p}}{T_{p}^{T}J_{p}T_{p}}}} - \begin{bmatrix}0 & 0 \\0 & {{{{mg}\left\lbrack n_{g} \right\rbrack}_{\times}\left\lbrack \zeta_{G} \right\rbrack}_{\times} + {\sum\limits_{p = 1}^{N_{p}}{\left\lbrack f_{p} \right\rbrack_{\times}\left\lbrack \zeta_{a,p} \right\rbrack}_{\times}}}\end{bmatrix}}},{where}} & (16) \\{J_{p} = {{{- {k_{p}\left( {1 - \frac{l_{p}}{\zeta_{{ba},p}}} \right)}}I} - {k_{p}\; \frac{l_{p}}{{\zeta_{{ba},p}}^{3}}\zeta_{{ba},p}\zeta_{{ba},p}^{T}}}} & (17) \\{f_{p} = {{- {k_{p}\left( {{\zeta_{{ba},p}} - l_{p}} \right)}}{\frac{\zeta_{{ba},p}}{\zeta_{{ba},p}}.}}} & (18)\end{matrix}$

The stiffness matrix K defined by Equation (16) is special in that itaccounts for all geometric stiffness effects caused by the gravitypreload.

A softly suspended rigid body 2 always performs free vibrations with sixdifferent mode shapes X_(j) and six natural frequencies ω_(j). The modeshapes X_(j) and natural frequencies ω_(j) can be obtained by solvingthe following eigenvalue problem. (Note that moderate viscous dampingdoes not affect the mode shapes and has only marginal effects on thenatural frequencies. Therefore, damping does not need to be taken intoaccount at this stage.)

0=(−ω_(j) ² M+K)X _(j) , j=1, . . . , 6   (19)

The mode shapes X_(j) should be normalized in a consistent way, e.g. insuch a way that

∥X_(j)∥=1.

In the next step, the mode shapes X_(j) obtained from Equation (19) aretransformed into the corresponding output s_(l) obtained by a givensensor 100. In the following this transformation is stated for threedifferent types of sensors 100 according to FIGS. 4 to 6. Note that ineach case at least N₁=6 senors must be used, when the rigid bodyperforms vibrations along the six degrees of freedom (preferably, theremust be as many sensors as degrees of freedom). According to FIG. 4,sensors 100 in the form of accelerometers are provided at differentpoints on the platform 30 or the rigid body 2 itself. In case theorientation of the accelerometer 100 is defined by a unit vector n₁ andits position in body-fixed coordinates is given by ζ₁ (cf. FIGS. 2 and3), the relationship between the measurement acceleration s₁ ⁽¹⁾ and therigid-body mode motion (movement) (δx, δθ) is

$\begin{matrix}{s_{l}^{(1)} = {A_{l}^{(1)}\begin{pmatrix}{\delta \; x} \\{\delta \; \theta}\end{pmatrix}}} & (20) \\{A_{l}^{(1)} = {- {{\omega_{j}^{2}\begin{bmatrix}n_{l}^{T} & \left( {\zeta_{l} \times n_{l}} \right)^{T}\end{bmatrix}}.}}} & (21)\end{matrix}$

Accelerometers 100 have the disadvantage that the stiffness and intertiaeffects of their cable connections 50 to the measurement (measuring)device 110 (computer 130) can distort the measurements.

A second possibility according to FIG. 5 is the use of force sensors 100placed between at least six of the elastic wires p and the carrier 10.For a sensor 100 pointing in a direction ñ₁ (in space-fixedcoordinates), the relationship between the rigid body motion (δx, δθ)and the sensor output s₁ ⁽²⁾ is defined by

$\begin{matrix}{s_{l}^{(2)} = {A_{l}^{(2)}\begin{pmatrix}{\delta \; x} \\{\delta \; \theta}\end{pmatrix}}} & (22) \\{A_{l}^{(2)} = {{\overset{\sim}{n}}_{l}^{T}{R(\theta)}{J_{l}(0)}{T_{l}.}}} & (23)\end{matrix}$

The matrices R(θ), J₁(0) and T₁ were already obtained as part ofcomputing the stiffness matrix K.

The use of space-fixed force sensors 100 according to FIG. 5 eliminatesthe need for cable connections to moving parts in the system.

A third possibility according to FIG. 6 is to integrate a number offorce sensors 100 into the upper part of the elastic elements(suspension wires) p. In this case, the following relationship definesthe sensor output S₁ ⁽³⁾ depending on the rigid body movement (δx, δθ):

$\begin{matrix}{s_{l}^{(3)} = {A_{l}^{(3)}\begin{pmatrix}{\delta \; x} \\{\delta \; \theta}\end{pmatrix}}} & (24) \\{A_{l}^{(3)} = {\frac{k_{l}}{\zeta_{{ba},l}}\zeta_{{ba},l}^{T}{T_{l}.}}} & (25)\end{matrix}$

Compared with sensors in the form of accelerometers, the motionamplitudes of this type of force sensor 100 is small, minimizingdistortions caused by cables 50. Unlike both accelerometers 100 (FIG. 4)and space-fixed force sensors 100 (FIG. 5), force sensors 100 that arepart of the elastic elements (suspension wires) p are always loaded inthe same direction; as a result, errors due to cross-sensitivity can beavoided.

The free vibration signal measured by a given sensor 100 is defined by

$\begin{matrix}{{s_{l}\left( t_{k} \right)} = {A_{l}{\sum\limits_{j = 1}^{6}{X_{j}{^{{- \zeta_{j}}\omega_{j}t_{k}}\left( {{a_{{2j} - 1}\sin \; \left( {\omega_{j}t_{k}} \right)} + {a_{2j}{\cos \left( {\omega_{j}t_{k}} \right)}}} \right)}}}}} & (26)\end{matrix}$

where ζ₁ is the damping ratio of the j-th rigid body mode. The factorsa_(2j−1) and a_(2j) define the amplitude and the phase of a given modeand are the only parameters that depend on the random initialexcitation.

Equation (26) defines the theoretical vibration signals of the rigidbody 2. This expression can be fitted to the measured time-domainsignals, ŝ₁(t_(k)), in order to identify the rigid body proportiesr_(s). The resulting optimization problem is defined by

$\begin{matrix}{\min\limits_{\substack{\begin{matrix}{r_{s} \in {\mathbb{R}}^{10}} \\{{\{ a_{j}\}} \in {\mathbb{R}}^{12}}\end{matrix} \\ {\{\zeta_{j}\}} \in {\mathbb{R}}^{6}}}{\sum\limits_{l = 1}^{N_{l}}{\sum\limits_{k = 1}^{N_{k}}\left( {{s_{l}\left( t_{k} \right)} - {{\overset{\bigvee}{s}}_{l}\left( t_{k} \right)}} \right)^{2}}}} & (27)\end{matrix}$

Note that the modal damping ratios ζ₁ and the scaling factors a_(2j−1)and a_(2j) must be identified at the same time as the rigid bodyproperties, even though these parameters may not be of interest to theexperimenter.

Conventional nonlinear least-squares routines (e.g. theGauss-Newton-Algorithms or the Leuvenberg-Marquardt Algorithms) can beused to solve the optimization problem Equation (27).

Preferably, all calculations in the course of the method according tothe ivention outlined above are performed by the analysing means 20,i.e., in particular by said computer 130 and said software carried outby said computer 130.

1. A system for determining inertia properties of a rigid body,particularly the inertia tensor, the mass and/or the position of thecenter of mass, comprising: a carrier, which is designed for suspendinga rigid body (S) from the carrier, such that the rigid body is able toperform movements along a number of degrees of freedom of the rigidbody, as many sensors as degrees of freedom of the rigid body providingoutput signals for detecting the movement of the rigid body along saidnumber of degrees of freedom of the rigid body, a measuring devicecooperating with the sensors, wherein the measuring device is configuredto measure said movement of the rigid body by means of said outputsignals (ŝ₁(t_(k))), and an analysing means configured for determiningfrom said output signals (ŝ₁(t_(k)))said inertia properties (r_(s)) ofthe rigid body.
 2. The system according to claim 1, wherein saidmovement corresponds to free vibrations along the number of degrees offreedom of the rigid body.
 3. The system according to claim 1, whereinthe measuring device is configured to measure output signals (ŝ₁(t_(k)))corresponding to the translation of the rigid body along the threeorthogonal axes and the rotations about these axes as a function of time(t_(k)).
 4. The system according to claim 1, wherein the analysing meansis configured to fit said measured output signal (ŝ₁(t_(k))) to thefunction${s_{l}\left( t_{k} \right)} = {A_{l}{\sum\limits_{j = 1}^{6}{X_{j}{{^{{- \zeta_{j}}\omega_{j}t_{k}}\left( {{a_{{2j} - 1}{\sin \left( {\omega_{j}t_{k}} \right)}} + {a_{2j}{\cos \left( {\omega_{j}t_{k}} \right)}}} \right)}.}}}}$5. The system according to claim 4, wherein the analysing means isconfigured to determine said inertia properties (r_(s)) by minimizingthe expression$\sum\limits_{l = 1}^{N_{l}}{\sum\limits_{k = 1}^{N_{k}}\left( {{s_{l}\left( t_{k} \right)} - {{\overset{\bigvee}{s}}_{l}\left( t_{k} \right)}} \right)^{2}}$with respect to r_(s) ∈

, {a_(j)} ∈

, and {ζ_(j)} ∈

, wherein the analysing means is particularly configured to conduct saidminimisation by means of a non-linear least-squares method.
 6. Thesystem according to claim 1, wherein the system comprises elasticelements (p), which are designed for suspending the rigid body from thecarrier, wherein the rigid body is suspended from the carrier via saidelastic elements (p), wherein in particular the elastic elements (p) aredesigned as wires and/or springs, wherein particularly one, two three,four, five, six, seven or eight elastic elements (p) are provided. 7.The system according to claim 6, wherein the system comprises a platformthat is designed for suspending the rigid body, wherein the platform issuspended from the carrier via said elastic elements (p) in order tosuspend the rigid body (S) from the carrier.
 8. The system according toclaim 1, wherein said sensors are arranged on said platform, on thecarrier, or form a part of an associated elastic element (p).
 9. Thesystem according to claim 1, wherein said carrier is designed as ahexahedral framework.
 10. A method for determining inertia properties ofa rigid body, particularly the inertia tensor, the mass and/or theposition of the center of mass, wherein in particular the systemaccording to one of the preceding claims is used for conducting themethod, the method comprising the steps of: suspending the rigid bodyfrom a carrier, forcing the rigid body to perform movements along anumber of degrees of freedom of the rigid body, measuring an outputsignal (ŝ₁(t_(k))) corresponding to said movement of the rigid bodyautomatically, and determining said inertia properties (r_(s)) from thesaid movement (ŝ₁(t_(k))) automatically, wherein particularly the rigidbody is forced to perform movements in the form of free vibrations,wherein particularly said output signal (ŝ₁(t_(k))) corresponds to thetranslation of the rigid body along three orthogonal axes and therotation of the rigid body about these axes as a function oftime(t_(k)), respectively.
 11. The method according to claim 10, whereinsaid measured output signal (ŝ₁(t_(k))) is automatically fitted to thefunction${s_{l}\left( t_{k} \right)} = {A_{l}{\sum\limits_{j = 1}^{6}{X_{j}{{^{{- \zeta_{j}}\omega_{j}t_{k}}\left( {{a_{{2j} - 1}{\sin \left( {\omega_{j}t_{k}} \right)}} + {a_{2j}{\cos \left( {\omega_{j}t_{k}} \right)}}} \right)}.}}}}$12. The method according to claim 11, wherein said inertia propertiesare automatically determined by minimizing the expression$\sum\limits_{l = 1}^{N_{l}}{\sum\limits_{k = 1}^{N_{k}}\left( {{s_{l}\left( t_{k} \right)} - {{\overset{\bigvee}{s}}_{l}\left( t_{k} \right)}} \right)^{2}}$with respect to r_(s) ∈

, {a_(j)} ∈

, {ζ_(j)} ∈

, wherein said minimisation is particularly automatically conducted bymeans of a non-linear least-squares method.
 13. The method according toclaim 10, wherein besides said measured output signals (ŝ₁(t_(k))),merely the following parameters are used to determine said inertiaproperties of said rigid body: the number (N_(p)) of the elasticelements (p), the stiffness value of the elastic elements (k_(p)), thelengths (l_(p)) of the unloaded elastic elements (p), the attachmentlocations (ζ_(a,p)) of the elastic elements (p) on the carrier,particularly in space-fixed coordinates, the attachment locations({tilde over (ζ)}_(b,p))of the elastic elements (p) on the platform orthe rigid body (S), particularly in body-fixed coordinates, theorientation of the field of gravity (ñ_(g)), and particularly theinertia properties (r_(p)) of the platform.